JP6082530B2 - transmission - Google Patents

Description

  The present invention relates to a transmission, and more particularly to a transmission capable of suppressing a shock of shifting while eliminating a time during which torque transmission is interrupted.

  2. Description of the Related Art Conventionally, there are known transmissions that perform gear shifting by arranging a plurality of meshing gear pairs set at different gear ratios on a pair of parallel shafts and selectively transmitting these gear pairs by a clutch device. ing. For example, Patent Document 1 discloses a transmission including a clutch device that transmits power by engagement of a ball member. According to the transmission disclosed in Patent Document 1, since the power transmission or interruption can be instantaneously switched by moving the ball member of the clutch device in the radial direction, the time during which the torque transmission is interrupted by the clutch device. Can be shortened.

JP 2009-74639 A

  However, in the above-described conventional technique, transmission or interruption of power is instantaneously switched by the clutch device, so that the change in the input rotational speed accompanying the change in the gear ratio occurs instantaneously. There is a problem that a shock due to inertia torque occurs with the rapid change of the input rotational speed.

  The present invention has been made to solve the above-described problems, and an object of the present invention is to provide a transmission that can suppress a shock of shifting while eliminating the time during which torque transmission is interrupted.

Means for Solving the Problems and Effects of the Invention

In order to achieve this object, according to the transmission according to claim 1 and 2, a plurality of gear pairs that mesh with each other and are arranged on a pair of parallel shafts, one of which is a first shaft and the other is a second shaft. The transmission gear ratio is set to be different. One gear of each of the plurality of gear pairs is supported so as to be rotatable relative to the shaft by a clutch device.

  The clutch device is configured such that power input from the first shaft is transmitted to the second shaft so as to be cut off, while transmission of power from the second shaft to the first shaft is cut off. The output system rotating member is configured to be relatively movable in the axial direction with respect to the input system rotating member, and an output track surface is formed on one of the inner peripheral surface and the outer peripheral surface of the output system rotating member. The input raceway surface is formed on one of the inner circumferential surface and the outer circumferential surface of the input system rotating member while facing the output raceway surface. A plurality of rollers are interposed between the input raceway surface and the output raceway surface, and the rollers are set at a predetermined skew angle with respect to the central axis of the input system rotation member. When the roller rotates in a predetermined direction, the roller revolves around the central axis while being rotated by being guided by the input raceway surface and the output raceway surface.

  Guided by the rotation of the roller, the input system rotating member and the output system rotating member move relative to each other in the direction in which the distance between the input track surface and the output track surface is reduced while being elastically deformed in the radial direction. As a result, the rollers engage with the input raceway surface and the output raceway surface, and power is transmitted from the first shaft to the second shaft. When the clutch device on the high speed stage side, which has been disengaged from the input raceway surface and the output raceway surface, and the roller is engaged by the switching means, the low speed stage clutch device to which torque has been transmitted so far becomes the one-way clutch. The roller engagement is automatically released. Therefore, it is possible to eliminate the time during which torque transmission is interrupted when changing the gear ratio.

  Here, when switching from the disengaged state to the engaged state by the switching means, the input system rotating member and the output system rotating member are elastically deformed in the radial direction, and the distance between the input track surface and the output track surface is reduced. The rollers move relative to each other in the axial direction, and the rollers engage with the input raceway surface and the output raceway surface. Since the input rotation member and the output rotation member are elastically deformed in the radial direction, the change in the input rotation speed accompanying the change in the gear ratio can be mitigated. Shock can be suppressed. Therefore, there is an effect that the shock of shifting can be suppressed while eliminating the time during which the torque transmission is interrupted.

The twisting direction of the gear pair is set so that the tooth traces are not parallel to the central axis. The twisting direction is determined by the direction of the axial force acting on the gear due to the meshing of the gear pair. The direction of movement of the input system rotating member or the output system rotating member in the axial direction when the rollers engage with the input track surface and the output track surface by narrowing the space between the track surfaces is set to be the same.

Here, when the rollers engage with the input raceway surface and the output raceway surface, the shafts of the input system rotation member and the output system rotation member are generated by the axial component of the frictional force generated between the input raceway surface, the output raceway surface, and the rollers. The pulling force in the direction is suppressed. If the axial component force increases, the distance between the input raceway surface and the output raceway surface cannot be sufficiently narrowed, and a predetermined torque may not be transmitted.

On the other hand, the twist direction of the gear teeth of the gear pair reduces the distance between the input raceway surface and the output raceway surface, and the input system rotating member or output in the axial direction when the rollers engage with the input raceway surface and the output raceway surface. By setting the direction of movement of the system rotation member to be the same, when the rollers are engaged with the input raceway surface and the output raceway surface and power is transmitted, the input system rotation member or output system is generated by the reaction force of the gear. The rotation member is promoted to move in the axial direction so as to narrow the distance between the input raceway surface and the output raceway surface. Thereby, the pulling force in the axial direction of the input system rotating member and the output system rotating member can be increased, and there is an effect that a predetermined torque can be reliably transmitted.

According to the transmission according to claim 3 and 4 , the clutch device includes an input system rotation member or an output system rotation in which gears are connected in a state where the engagement between the input raceway surface and the output raceway surface and the roller is released. An inlay portion that fits into the member is provided. The inlay portion has a radial clearance between the input system rotating member or the output system rotating member that allows the rollers to roll when the input track surface and the output track surface engage with the rollers. Therefore, it is possible to suppress the engagement of the input raceway surface and the output raceway surface with the rollers by the inlay portion. In addition, in a state where the engagement between the input raceway surface and the output raceway surface and the roller is released, the radial movement of the input system rotation member or the output system rotation member is restricted, so that the gears are relative to the clutch device. This has the effect of preventing abnormal noise that occurs when rotating.

According to the transmission of claims 5 and 6, the shaft of the input system rotating member or the output system rotating member to which the gears are connected in a state where the engagement between the input raceway surface and the output raceway surface and the roller is released. Movement to one side of the direction is restricted by the movement restricting portion, and an urging force in the axial direction toward the movement restricting portion is applied to the input system rotating member or the output system rotating member by the urging means. Thus, in the state where the engagement between the input raceway surface and the output raceway surface and the roller is released, the axial movement of the input system rotation member or the output system rotation member is restricted, and the clutch device is kept in the non-engagement state. be able to.

Thereby, even when the shift system member or the control system breaks down, it has a fail-safe function and is effective in preventing double meshing in which a plurality of gear pairs are simultaneously engaged. In addition, the clutch device other than the gear pair to which torque is transmitted is kept in the non-engaged state without inputting an electric signal, so that it is possible to reduce power consumption and reduce friction.

According to the transmission of the seventh and eighth aspects, at least one of the input system rotating member and the output system rotating member is attached by the elastic member in a direction in which the input track surface and the output track surface can be engaged with the roller. Be forced. Thereby, there exists an effect which can make a clutch apparatus engage easily. On the other hand, when the input system rotating member or the output system rotating member is moved in the axial direction by the switching means against the biasing force of the elastic member, the engagement between the input track surface and the output track surface and the roller is released. Therefore, there is an effect that the engagement between the input raceway surface and the output raceway surface and the roller can be reliably released.

Input track surface and the output track surface may be formed as a single sheet hyperboloid of revolution or conical surface that contacts the outer peripheral surface of the roller and the line. With input raceway surface and the output raceway surface shapes simple conical surface of, there is an effect of the pressurized Engineering easily. In addition, by making the input raceway surface and the output raceway surface a single leaf rotation hyperboloid, it is easier to make a contact between the roller having the skew angle and the raceway surface than in the case where the raceway surface is a conical surface. As a result, the durability can be improved.

In the set gear pair to a Jo Tokoro shift ratio, power is transmitted by the roller is engaged with the input track surface and the output track surface by the clutch device. When shifting up, in the gear pair having a gear ratio smaller than the gear ratio of the gear pair to which power is transmitted, the input track is changed from the state where the engagement between the input track surface and the output track surface and the roller is released by the switching means. side and output raceway surface and the roller can Rukoto switched to a state of engagement. When the power is transmitted from the gear pair having a small gear ratio after being shifted up, the rotation speed of the second shaft increases as compared to before the shift up. As a result, in the clutch device in the gear pair to which power was transmitted before the upshift, the output system rotating member rotates relative to the input system rotating member, so that it acts as a one-way clutch and automatically Is interrupted. As a result, the shifting can be performed by switching from the state where the engagement between the input raceway surface and the output raceway surface and the roller is released to the state where the input raceway surface and the output raceway surface are engaged with the roller. As a result, there is an effect that can be eliminated time for the torque transmission is interrupted when the sheet Futoappu.

Transfer input raceway surface by moving mechanism and the output track surface and the roller allowed the movement of the input system rotating member or the output system rotating member in the axial position that enables or nonengageable engagement, the output system rotates from the input system rotating member Transmission of power to the member can be cut off. As a result, there is an effect of blocking can transmit the power from the input system rotating member to the output system rotating member.

It is a skeleton figure which shows typically the transmission in 1st Embodiment. It is an axial sectional view of a clutch device. (A) is a schematic side view which shows the positional relationship of a cam shaft and a pin, (b) is a schematic front view of a cam shaft. (A) is a perspective view of the input system rotating member and the first cage showing the arrangement of the first rollers, and (b) is a perspective view of the input system rotating member and the second cage showing the arrangement of the second rollers. is there. (A) is the half sectional view of the clutch apparatus which moved the cam shaft to the axial direction, (b) is a half sectional view of the clutch apparatus in which the 1st roller is in an engagement state. (A) is a development view of the input track surface and the output track surface, and (b) is a schematic diagram of the input track surface and the output track surface in which the first roller is engaged. (A) is the half sectional view of the clutch apparatus which moved the cam shaft to the axial direction, (b) is a half sectional view of the clutch apparatus in which the 2nd roller is in an engagement state. (A) is a schematic diagram which shows the rotation direction and thrust direction in meshing of a gear pair, (b) is a schematic diagram which shows the rotation direction and thrust direction in meshing of a gear pair. (A) is the half sectional view of the clutch apparatus which comprises the transmission in 2nd Embodiment, (b) is a half sectional view of the clutch apparatus which moved the cam shaft to the axial direction, (c) is It is a half sectional view of the clutch device in which the first roller is in an engaged state. (A) is a half sectional view of the clutch device in which the camshaft is moved in the axial direction, (b) is a half sectional view of the clutch device in which the second roller is engaged, and (c) is the first side view. It is a half sectional view of a clutch device in the state where engagement of a roller was released. (A) is the half sectional view of the clutch apparatus which comprises the transmission in 3rd Embodiment, (b) is a half sectional view of the clutch apparatus in which the 1st roller is an engagement state, (c) is It is a half sectional view of the clutch device in which the second roller is in an engaged state. (A) is a skeleton diagram schematically showing the transmission according to the fourth embodiment, and (b) is a schematic diagram showing a rotation direction and a thrust direction in the meshing of the gear pair.

  Hereinafter, preferred embodiments of the present invention will be described with reference to the accompanying drawings. First, with reference to FIG. 1, the transmission 1 in 1st Embodiment mounted in a vehicle is demonstrated. FIG. 1 is a skeleton diagram schematically showing the transmission 1 in the first embodiment. The transmission 1 is a device for changing the ratio of the rotational speed of the drive shaft 2 to which the power of a power source such as an engine is input and outputting it to the output shaft 5. The transmission 1 includes an input shaft 4 connected to a drive shaft 2 via a main clutch 3, an output shaft 5 disposed in parallel to the input shaft 4, and the output shaft 5 and the input shaft 4. A plurality of gear pairs 7, 8, 9, 10, 11, 12, 13, and 14 set so as to mesh with each other to have different gear ratios are configured. The power transmitted to the output shaft 5 is transmitted to the differential device 15 to drive the wheels 16.

  The gear pairs 7, 8, 9, 10, 11, 12, 13 and 14 are arranged on the input shaft 4 and are driven by the power input from the drive shaft 2 to the input shaft 4 by connecting the main clutch 3. Drive gears 7a, 8a, 9a, 10a, 11a, 12a, 13a, 14a, and driven gears disposed on the output shaft 5 and driven by the drive gears 7a, 8a, 9a, 10a, 11a, 12a, 13a, 14a 7b, 8b, 9b, 10b, 11b, 12b, 13b, 14b. Here, the gear pairs 7, 8, 9, 10, 11, 12, 13, 14 have the largest gear ratio (the number of teeth of the driven gear ÷ the number of teeth of the driving gear), and the first to the first gears in order from the driving shaft 2. The eighth speed is set, the gear pair 7 is the first speed, and the gear pair 14 is the eighth speed. The reverse gear pair 6 includes a drive gear 6a disposed on the input shaft 4 and a driven gear 6b that transmits the rotational power of the drive gear 6a to the output shaft 5 via an idler gear.

  The driven gears 6 b, 7 b, 8 b, 9 b, 10 b, 11 b, 12 b, 13 b, 14 b are each formed integrally with the output shaft 5. On the other hand, the drive gears 6a, 7a, 8a, 9a, 10a, 11a, 12a, 13a, and 14a are respectively disposed on the input shaft 4 via a clutch device 20 described later. The clutch device 20 is a device that interrupts transmission of power from the output shaft 5 to the input shaft 4 while transmitting power from the input shaft 4 to the output shaft 5 so as to be cut off. The clutch device 20 includes a camshaft 50 penetrating in the axial direction of the input shaft 4 and a camshaft 50 by applying a rotational force to the camshaft 50 in order to interrupt transmission of power from the input shaft 4 to the output shaft 5. And a driving device 60 that linearly moves 50 in the axial direction.

  Here, the detailed configuration of the clutch device 20 will be described with reference to FIGS. FIG. 2 is an axial sectional view of the clutch device 20. 2, the clutch device 20 connected to the drive gears 7a and 8a is illustrated, and the illustration of the clutch device 20 connected to the other drive gears 6a, 9a, 10a, 11a, 12a, 13a, and 14a is omitted. doing. In order to facilitate understanding, illustration of a thrust bearing and the like that receive an axial force and illustration of teeth formed on the drive gears 7a and 7b are omitted.

  As shown in FIG. 2, the clutch device 20 is disposed on a first inner ring 24 as an input system rotating member for transmitting power from the input shaft 4 to the drive gear 7 a, and on the outer peripheral side of the first inner ring 24. A first outer ring 29 as an output system rotating member formed integrally with the drive gear 7a, and a plurality of first rollers 27 interposed between the first inner ring 24 and the first outer ring 29 are configured. Yes. The clutch device 20 is disposed on the outer peripheral side of the second inner ring 34 as an input system rotating member for transmitting power from the input shaft 4 to the driving gear 8a, and on the driving gear 8a. A second outer ring 39 as an output system rotating member formed integrally, and a plurality of second rollers 37 interposed between the second inner ring 34 and the second outer ring 39 are configured. Since the first inner ring 24, the second inner ring 34, the first outer ring 29, and the second outer ring 39 are arranged in parallel in the clutch device 20, the axial length of the clutch device 20 can be reduced, and consequently the transmission 1. The axial length can be reduced.

  The first inner ring 24 is a member that has a function of transmitting the rotational power of the input shaft 4 to the drive gear 7a, and an input raceway surface 25 that forms a single leaf hyperboloid around the central axis O is formed on the outer peripheral surface. Yes. The first inner ring 24 is restricted from rotating with respect to the input shaft 4 by the spline 24 a, and is allowed to move in the axial direction with respect to the input shaft 4. The stoppers 21 and 22 are members for restricting the axial movement of the first inner ring 24 exceeding a predetermined amount. The stoppers 21 and 22 are arranged on the outer periphery of the input shaft 4 with a predetermined distance from the axial end surface of the first inner ring 24. The first inner ring 24 protrudes outward in the axial direction of the axial end surface. The first inner ring 24 is urged to one axial side (the right side in FIG. 2) by a disc spring 26 disposed between the stopper 21 and the first inner ring 24 so that the axial end surface is in contact with the stopper 22. Thus, the diameter of the input raceway surface 25 is reduced toward the stopper 21 side.

  The first outer ring 29 is a member having a function for transmitting the power of the input shaft 4 to the drive gear 7a together with the first inner ring 24, and the output raceway surface 30 forming a single-leaf rotating hyperboloid around the central axis O is formed on the inner periphery. Formed on the surface. The first outer ring 29 is configured to be rotatable relative to the first inner ring 24 and to be relatively movable in the axial direction. The first outer ring 29 has an inner peripheral surface 31 fitted to a spigot portion 21 a formed on the outer peripheral surface of the stopper 21, and a flange portion 21 b (movement restricting portion) and a stopper 22 formed on the radially outer side of the stopper 21. The movement in the axial direction exceeding a predetermined amount is restricted. The stoppers 21 and 22 stop the axial movement of the first inner ring 24 and the first outer ring 29 at fixed positions when the first roller 27 is engaged and screwed into the input raceway surface 25 and the output raceway surface 30. And a function of a torque limiter that prevents a torque exceeding a certain level from being applied, and a function of preventing the first roller 27 from coming off.

  The first outer ring 29 is urged to the other side in the axial direction (left side in FIG. 2) by a coil spring 33 disposed between the first outer ring 29 and the second outer ring 39 so that the axial end surface 32 abuts against the flange portion 21b. ing. The coil spring 33 is a member for biasing the first outer ring 29 in the axial direction so as to widen the distance between the input raceway surface 25 and the output raceway surface 30.

  The second inner ring 34 is a member that has a function of transmitting the rotational power of the input shaft 4 to the drive gear 8a, and an input raceway surface 35 that forms a single-leaf rotating hyperboloid around the central axis O is formed on the outer peripheral surface. Yes. The second inner ring 34 is restricted from rotating with respect to the input shaft 4 by the spline 34 a, and is allowed to move in the axial direction with respect to the input shaft 4. The stoppers 22 and 23 are members for restricting movement of the second inner ring 34 in the axial direction exceeding a predetermined amount. The stoppers 22 and 23 are arranged on the outer periphery of the input shaft 4 with a predetermined distance from the axial end surface of the second inner ring 34. The second inner ring 34 projects outwardly in the axial direction of the axial end surface. The second inner ring 34 is urged toward the other side (left side in FIG. 2) in the axial direction by a disc spring 36 disposed between the stopper 23 and the second inner ring 34 so that the end face in the axial direction contacts the stopper 22. The input raceway surface 35 is reduced in diameter toward the stopper 23 side.

  The second outer ring 39 is a member responsible for the function of transmitting the power of the input shaft 4 to the drive gear 8a together with the second inner ring 34, and the output raceway surface 40 forming a single leaf rotating hyperboloid around the central axis O is formed on the inner periphery. Formed on the surface. The second outer ring 39 is configured to be rotatable relative to the second inner ring 34 and relatively movable in the axial direction. The second outer ring 39 has an inner peripheral surface 41 fitted to a spigot portion 23 a formed on the outer peripheral surface of the stopper 23, and a flange portion 23 b (movement restricting portion) and a stopper 22 formed on the radially outer side of the stopper 23. The movement in the axial direction exceeding a predetermined amount is restricted. The stoppers 22 and 23 stop the axial movement of the second inner ring 34 and the second outer ring 39 at fixed positions when the second roller 37 is engaged and screwed into the input raceway surface 35 and the output raceway surface 40. And having a function of a torque limiter that prevents a torque exceeding a certain level from being applied, and a function of preventing the second roller 37 from coming off.

  The second outer ring 39 is biased to one axial side (the right side in FIG. 2) by the coil spring 33 disposed between the second outer ring 39 and the axial end face 42 against the flange 23b. ing. The coil spring 33 is a member for biasing the second outer ring 39 in the axial direction so as to widen the distance between the input raceway surface 35 and the output raceway surface 40.

  The input shaft 4 has a camshaft 50 extending therethrough in the axial direction. The camshaft 50 is a member for causing the pins 61 and 62 to appear in and out of the outer periphery of the input shaft 4 by the cam portion 51 formed on the outer periphery by being moved in the axial direction by the drive device 60 (see FIG. 1). . The pins 61 and 62 are members that extend in the radial direction of the input shaft 4. When the tips are pushed up by the cam portion 51 and the tips protrude from the outer periphery of the input shaft 4, the inner periphery of the first inner ring 24 and the second inner ring 34. The tip is pressed against the inclined surfaces 24b and 34b formed on the surface. The axial force of the first inner ring 24 and the second inner ring 34 due to the pins 61 and 62 being pressed against the inclined surfaces 24b and 34b of the first inner ring 24 and the second inner ring 34 is the biasing force (shaft of the disc springs 26 and 36). Therefore, the first inner ring 24 moves to the stopper 21 side (left side in FIG. 2) against the biasing force of the disc springs 26, 36, and the second inner ring 34 moves to the stopper 23 side (see FIG. 2). 2 right).

  The camshaft 50 will be further described with reference to FIG. FIG. 3A is a schematic side view showing the positional relationship between the camshaft 50 and the pins 61 to 64, and FIG. 3B is a schematic front view of the camshaft 50. In FIG. 3A, a part of the camshaft 50 in the longitudinal direction is not shown.

  As shown in FIGS. 3A and 3B, the cam portion 51 is formed on the outer periphery of the camshaft 50 in a line symmetrical manner with the central axis O as the symmetry axis. The cam portions 52, 53, 54, and 55 are arranged so as to be shifted in the axial direction and the circumferential direction with respect to the other cam portions 51 to 55, respectively, and as shown in FIG. Are formed on the outer periphery of the camshaft 50 in a line symmetrical manner with the central axis O as the axis of symmetry. The cam part 51 is a part for projecting and retracting the pins 61 and 62, and the cam part 52 is a part for projecting and retracting the pins 63 and 64. The clutch device 20 disposed corresponding to the drive gears 7a and 8a (see FIG. 1) is operated by the protrusions and recesses of the pins 61 and 62, and is disposed corresponding to the drive gears 9a and 10a by the protrusions and recesses of the pins 63 and 64. The operated clutch device 20 is operated.

  The cam part 53 is a part for operating the clutch device 20 arranged corresponding to the drive gears 11a, 12a, and the cam part 54 is used for operating the clutch device 20 arranged corresponding to the drive gears 13a, 14a. It is a part for operation. The cam portion 55 is a portion for operating the first clutch 20 disposed corresponding to the drive gear 6a (reverse gear). As described above, the cam portions 51, 52, 53, 54, and 55 are displaced from each other in the axial direction and the circumferential direction with respect to the other cam portions 51 to 55. The pins arranged corresponding to the drive gears 7a to 14a are pushed up by the cam portions 51, 52, 53, 54, and 55 and protrude from the input shaft 4 one by one.

  Next, the first roller 27 and the second roller 37 will be described with reference to FIG. 4A is a perspective view of the input system rotating member (first inner ring 24) and the first cage 28 showing the arrangement of the first rollers 27, and FIG. 4B shows the arrangement of the second rollers 37. FIG. 4 is a perspective view of an input system rotating member (second inner ring 34) and a second retainer 38. FIG.

  As shown in FIG. 4A, the first roller 27 is a member formed in a cylindrical shape, and is held between the input raceway surface 25 (see FIG. 2) and the output raceway surface 30 by the first cage 28. Is done. The first cage 28 is a member for holding the first rollers 27 spaced from each other so that the first rollers 27 can smoothly rotate without interfering with each other. The first roller 27 is inclined at a constant angle α (for example, 15 °) from the plane including the central axis O (set to a constant skew angle α with respect to the central axis O), and the input raceway surface 25 and the output raceway surface 30. Are arranged in such a manner that their outer peripheral surfaces can come into linear contact with the input track surface 25 and the output track surface 30 (line contact).

  As shown in FIG. 4B, the second roller 37 is a member formed in a cylindrical shape, and is held between the input raceway surface 35 (see FIG. 2) and the output raceway surface 40 by the second cage 38. Is done. The second cage 38 is a member for holding the second rollers 37 spaced apart from each other so that the second rollers 37 rotate smoothly without interfering with each other. The second rollers 37 are inclined by a certain angle α (for example, 15 °) from the plane including the central axis O (skew angle α), and a plurality of second rollers 37 are arranged in the circumferential direction of the input raceway surface 35 and the output raceway surface 40. An outer peripheral surface is arranged to be linearly contactable with the raceway surface 35 and the output raceway surface 40.

  Returning to FIG. The drive gears 7a and 8a are members for transmitting the power transmitted to the first outer ring 29 and the second outer ring 39 to the driven gears 7b and 8b (see FIG. 1) to be engaged, respectively. The second outer ring 39 is integrally formed or coupled, and has a plurality of teeth on the outer peripheral surface, and the tooth streaks are formed so as to be non-parallel to the central axis O. Similarly, the driven gears 7 b and 8 b have a plurality of teeth on the outer peripheral surface, and the tooth lines are formed so as to be non-parallel to the central axis O. In the present embodiment, the drive gears 7a and 8a and the driven gears 7b and 8b are formed as a pair of helical gears that engage with each other.

  The distance between the stoppers 21 and 22 and the flange portion 21b is such that the axial end surface of the first inner ring 24 comes into contact with the stopper 22 by the biasing force of the disc spring 26 and the coil spring 33 and the axial end surface of the first outer ring 29 is It is set so that the outer peripheral surface of the first roller 27 does not come into contact with at least one of the input raceway surface 25 and the output raceway surface 30 when abutting against the portion 21b. In this case, the first roller 27 cannot be engaged with the input raceway surface 25 and the output raceway surface 30. On the other hand, when the camshaft 50 is moved to one axial side (the right side in FIG. 2) and the first inner ring 24 is moved to the stopper 21 against the biasing force of the disc spring 26, the input track The distance between the surface 25 and the output raceway surface 30 is narrowed, and the first roller 27 is set in linear contact with the input raceway surface 25 and the output raceway surface 30.

  The distance between the stoppers 22 and 23 and the flange 23b is such that the axial end surface of the second inner ring 34 abuts against the stopper 22 by the biasing force of the disc spring 36 and the coil spring 33 and the axial end surface of the second outer ring 39 Is set so that the outer peripheral surface of the second roller 37 does not come into contact with at least one of the input raceway surface 35 and the output raceway surface 40. In this case, the second roller 37 cannot be engaged with the input raceway surface 35 and the output raceway surface 40. On the other hand, when the camshaft 50 is moved to one axial side (right side in FIG. 2) and the second inner ring is moved to the stopper 23 against the biasing force of the disc spring 36, the input raceway surface The distance between the output track surface 40 and the output track surface 40 is reduced, and the second roller 37 is set in linear contact with the input track surface 35 and the output track surface 40.

  The operation of the transmission 1 configured as described above will be described with reference to FIGS. 5A is a half sectional view of the clutch device 20 in which the camshaft 50 is moved in the axial direction, and FIG. 5B is a half sectional view of the clutch device 20 in which the first roller 27 is engaged. 6A is a development view of the input raceway surface 25 and the output raceway surface 30, and FIG. 6B is a schematic diagram of the input raceway surface 25 and the output raceway surface 30 in which the first roller 27 is engaged. FIG. 7A is a half sectional view of the clutch device 20 in which the camshaft 50 is moved in the axial direction, and FIG. 7B is a half sectional view of the clutch device 20 in which the second roller 37 is engaged. is there. 6 (a) and 6 (b), the first roller 27 and the first outer ring 29 rotated by the torque of the first inner ring 24 are replaced with the first roller 27 'and the first outer ring 29' (two-dot chain line). ).

  As shown in FIG. 5A, when traveling at the first speed, the camshaft 50 is moved to one axial side (right side in FIG. 5A) with the main clutch 3 (see FIG. 1) connected. Then, the pin 61 is pushed up by the cam portion 51, the inclined surface 24b is pushed by the pin 61, and the first inner ring 24 is moved to the stopper 21 side. Thereby, the space | interval of the input track surface 25 and the output track surface 30 becomes narrow, and the 1st roller 27 contacts the input track surface 25 and the output track surface 30 linearly. When the first inner ring 24 rotates in one direction (the direction of the arrow Ri in FIGS. 4A and 6A) by the rotational drive of the input shaft 4, the first roller 27 rotates as shown in FIG. 6B. However, the input raceway surface 25 is revolved (clockwise in FIG. 4B). The first roller 27 and the output raceway surface 30 are displaced (l and L) in the radial direction (up and down direction in FIG. 6B) by the rotation of the first roller 27, and the output raceway surface 30 is radially moved by the displacement. It moves in the direction of arrow K (see FIG. 6A) while elastically deforming.

  As a result, the first outer ring 29 rotates in the direction of the arrow Ro shown in FIG. 6A, and in the direction of the arrow C in the axial direction (the distance between the input track surface 25 and the output track surface 30 (hereinafter referred to as “track interval”). Relative movement in the direction of narrowing). Since the movement of the first inner ring 24 in the axial direction is restricted by the stopper 21 and the pin 61, the first outer ring 29 moves against the urging force of the coil spring 33 as shown in FIG. 5B. In the direction of narrowing (right side of FIG. 5B). As a result, the first roller 27 is engaged with the input raceway surface 25 and the output raceway surface 30, and power is transmitted from the first inner ring 24 to the first outer ring 29.

  As a result, the rotational power of the input shaft 4 is transmitted to the drive gear 7a, and the driven gear 7b (see FIG. 1) that meshes with the drive gear 7a rotates. The other drive gears 8 a to 14 a idle the input shaft 4 because the first roller 27 or the second roller 37 cannot be engaged with the input raceway surface 25 and the output raceway surface 30 of each clutch device 20. As a result, the rotational speed α1 of the output shaft 5 becomes a speed corresponding to the gear ratio of the gear pair 7.

  When the relative movement of the first outer ring 29 in the axial direction is restricted at a predetermined position (the position of the stopper 21), the distance between the tracks in the axial direction is not reduced any further, and the elastic deformation of the first outer ring 29 in the radial direction is continued. Therefore, a torque larger than the torque (predetermined value) that can be transmitted at the track interval cannot be transmitted. As a result, the first inner ring 24 and the first outer ring 29 can be relatively rotated with a torque larger than a predetermined value. That is, the clutch device 20 functions as a torque limiter.

  Next, as shown in FIG. 7A, when shifting up from the first speed traveling state to the second speed, the camshaft 50 is connected to the one side in the axial direction with the main clutch 3 (see FIG. 1) connected. (The right side in FIG. 7A), the pin 62 is pushed up by the cam portion 51 instead of the pin 61, the inclined surface 34b is pushed by the pin 62, and the second inner ring 34 is moved to the stopper 23 side. Thereby, the space | interval of the input track surface 35 and the output track surface 40 becomes narrow, and the 2nd roller 37 contacts the input track surface 35 and the output track surface 40 linearly. When the second inner ring 34 is rotated in one direction (the direction of arrow Ri in FIG. 4B) by the rotational drive of the input shaft 4, the second raceway 37 revolves around the input raceway surface 35 while rotating. The second roller 37 and the output raceway surface 40 are displaced in the radial direction (the vertical direction in FIG. 7A) by the rotation of the second roller 37, and the output raceway surface 40 is elastically deformed in the radial direction by the displacement and is stopped. Move in the axial direction on the 22 side.

  As a result, the second outer ring 39 rotates around the second inner ring 34 and relatively moves in the direction of narrowing the interval (track interval) between the input raceway surface 35 and the output raceway surface 40. Since the movement of the second inner ring 34 in the axial direction is restricted by the stopper 23 and the pin 62, the second outer ring 39 moves against the urging force of the coil spring 33 as shown in FIG. 7B. Is moved in the direction of narrowing (left side in FIG. 7B). As a result, the second roller 37 is engaged with the input raceway surface 35 and the output raceway surface 40, and power is transmitted from the second inner ring 34 to the second outer ring 39. As a result, the rotational power of the input shaft 4 is transmitted to the drive gear 8a, and the driven gear 8b (see FIG. 1) that meshes with the drive gear 8a rotates. Since the rotational speed α2 of the second speed driven gear 8b is faster than the rotational speed α1 of the first speed driven gear 7b, the output shaft 5 rotates at a rotational speed α2 (> α1) corresponding to the gear ratio of the gear pair 8. To do.

  On the other hand, in the first speed gear pair 7, the first inner ring 24 rotates relative to the first outer ring 29 of the clutch device 20 in the opposite direction (the counter arrow Ri direction in FIG. 4A). The first inner ring 24 and the first outer ring 29 move relative to each other in a direction away from each other in the axial direction by a pulling-off force (a force for moving in the direction of increasing the track interval) due to the rotation of the roller 27. The biasing force of the disc spring 26 and the coil spring 33 assists the relative movement of the first outer ring 29 and the first inner ring 24 in the axial direction. As a result, the engagement between the input raceway surface 25 and the output raceway surface 30 and the first roller 27 is released, and the first inner ring 24 and the first outer ring 29 can be rotated relative to each other (free rotation). Idles the input shaft 4. In the other gear pairs 9 to 14 (3rd to 8th), the gears can be similarly changed by switching the clutch device 20.

  As described above, when the clutch device 20 is switched from the disengaged state of the input raceway surface 35 and the output raceway surface 40 to the second roller 37 during the upshifting, While the inner ring 34 and the second outer ring 39 are elastically deformed in the radial direction, the inner ring 34 and the second outer ring 39 are relatively moved in the axial direction in a direction in which the distance between the input raceway surface 35 and the output raceway surface 40 is reduced. As a result, the second roller 37 is engaged with the input raceway surface 35 and the output raceway surface 40. Since the second inner ring 34 and the second outer ring 39 are elastically deformed in the radial direction, the change in the input rotation speed accompanying the change in the gear ratio can be alleviated. Shock can be suppressed.

  Further, when the power is transmitted from the gear pair 8 by shifting up from the first speed to the second speed, the rotation speed of the output shaft 5 increases compared to before the shift up. As a result, the first outer ring 29 rotates relative to the first inner ring 24 in the clutch device 20 in the gear pair 7 to which power has been transmitted before the upshift (the first outer ring 29 is driven relative to the first inner ring 24). Side). Thereby, in the clutch device 20 in the gear pair 7, the transmission of power is cut off by the action of the one-way clutch. The pair of gears 7 and 8 are prevented from meshing with each other, and power is transmitted from the pair of gears 8 to the output shaft 5. Thus, since the power transmission of the clutch device 20 can be switched only by moving the camshaft 50 in the axial direction, the switching means (switching mechanism) of the transmission 1 can be simplified. Further, since the camshaft 50 is provided in the input shaft 4, the transmission 1 can be made compact.

  Further, since shifting (shifting up) can be performed simply by moving the camshaft 50 in the axial direction while the main clutch 3 (see FIG. 1) is connected, the time during which torque transmission is interrupted can be eliminated, It is possible to suppress a feeling of deceleration without causing the driver to feel a driving force loss (so-called torque loss) at the time of shifting.

  When the engagement between the input raceway surface 25 and the output raceway surface 29 and the first roller 27 is released (see FIG. 7B), the camshaft 50 is moved in the axial direction and is inclined by the pin 61. Since the pressing of 24 b is released, the first inner ring 24 is moved to the stopper 22 side and the first outer ring 29 is moved to the stopper 21 side by the biasing force of the disc spring 26 and the coil spring 33. Since the first roller 27 does not contact at least one of the input raceway surface 25 and the output raceway surface 30, the first roller 27 cannot be engaged with the input raceway surface 25 and the output raceway surface 30. As a result, transmission of power from the first inner ring 24 to the first outer ring 29 can be interrupted.

  In addition, the clutch device 20 includes an inlay portion 21 a that fits with the inner peripheral surface 31 of the first outer ring 29 in a state where the engagement between the input raceway surface 25 and the output raceway surface 30 and the first roller 27 is released. Yes. The inlay portion 21 a has a radial clearance that allows the first roller 27 to roll when the input raceway surface 25 and the output raceway surface 30 are engaged with the first roller 27, and the inner peripheral surface of the first outer ring 29. 31. It is possible to suppress the engagement between the input raceway surface 25 and the output raceway surface 30 and the first roller 27 from being hindered by the spigot portion 21a by the radial clearance. Furthermore, in the state where the engagement between the input raceway surface 25 and the output raceway surface 30 and the first roller 27 is released, the movement of the first outer ring 29 in the radial direction is restricted by the inlay portion 21a. On the other hand, when the drive gear 7a is idling, it is possible to prevent abnormal noise (rattle) caused by vehicle vibration or friction. Further, the inlay portion 23a can also prevent abnormal noise (rattle) in the second outer ring 39.

  Further, in a state where the engagement between the input raceway surface 25 and the output raceway surface 30 and the first roller 27 is released, the movement of the first outer ring 29 to one side in the axial direction is restricted by the flange portion 21b, and the coil spring An urging force in the axial direction toward the flange portion 21 b is applied to the first outer ring 29 by 33. As a result, the first outer ring 29 is brought into contact with the axial end surface of the first outer ring 29 and the flange portion 21b in a state where the engagement between the input raceway surface 25 and the output raceway surface 35 and the first roller 27 is released. Therefore, when the drive gear 7a is idling with respect to the input shaft 4, the clutch device 20 (first roller 27) can be kept in a non-engaged state.

  As a result, even when a shift system member such as the camshaft 50 or a control system such as the drive device 60 fails, it has a fail-safe function and prevents double meshing in which a plurality of gear pairs 7 to 14 are simultaneously engaged. it can. Further, the clutch device 20 (first roller 27) other than the gear pair to which torque is transmitted can be kept in the non-engaged state by the coil spring 33 without inputting an electric signal to the control system. Consumption can be suppressed, the apparatus configuration can be simplified, and friction can be reduced.

  Next, the rotational direction of the gear pairs 7 and 8 and the axial force (thrust) acting on the clutch device 20 will be described with reference to FIG. FIG. 8A is a schematic diagram showing the rotation direction and the thrust direction in the meshing of the gear pair 7, and FIG. 8B is a schematic diagram showing the rotation direction and the thrust direction in the meshing of the gear pair 8. 8A and 8B illustrate the drive gears 7a and 8a formed on the outer peripheral surfaces of the first outer ring 29 and the second outer ring 39 and the driven gears 7b and 8b engaged therewith. The first inner ring 24, the second inner ring 34, the first roller 27, the second roller 37, etc. are not shown, and the teeth 7a1, 8a1, 7b1 formed on the drive gears 7a, 8a and the driven gears 7b, 8b, respectively. , 8b1 is partially omitted.

  When shifting up from the first speed to the second speed, the second roller 37 is brought into linear contact with the input raceway surface 35 (see FIG. 7A) and the output raceway surface 40, as shown in FIG. ), When the input shaft 4 is relatively rotated in one direction (the direction of the arrow Ri in FIG. 8B), the second roller 37 is engaged with the input raceway surface 30 and the output raceway surface 40 as described above. Power is transmitted from the second inner ring 34 to the second outer ring 39 (arrow Ro is the direction of rotation of the second outer ring 39). When the drive gear 8a is driven by the power transmitted to the second outer ring 39 (the rotation direction is the arrow Ro direction), the rotation is transmitted to the driven gear 8b and the output shaft 5 (the rotation direction is the arrow Rt direction). Axial forces in certain directions (in the direction of arrow A and the direction of arrow P in FIG. 8B) are generated in the driving gear 8a and the driven gear 8b, respectively. The direction of the tooth traces of the drive gear 8a and the driven gear 8b is such that the direction of the axial force acting on the drive gear 8a (the direction of arrow A in FIG. 8B) narrows the distance between the input raceway surface 35 and the output raceway surface 40. Is set to be the same as the moving direction of the second outer ring 39 in the axial direction (direction of arrow A in FIG. 8B).

  Here, the axial component of the frictional force generated on the input raceway surface 35 and the output raceway surface 40 and the second roller 37 is the first when the second roller 37 is engaged with the input raceway surface 35 and the output raceway surface 40. The pulling force in the axial direction of the two inner rings 34 and the second outer ring 39 is suppressed, and this causes a predetermined torque to not be transmitted from the second inner ring 34 to the second outer ring 39. On the other hand, according to the clutch device 20, in addition to the pulling force of the input raceway surface 35 and the output raceway surface 40 due to the rotation of the second roller 37, the second outer ring 39 is caused by the axial force due to the reaction force of the driven gear 8b. Movement in the axial direction is promoted so as to reduce the distance between the input raceway surface 35 and the output raceway surface 40. As a result, since the pulling force in the axial direction of the second inner ring 34 and the second outer ring 39 can be increased, the clutch device 20 can reliably transmit a predetermined torque.

  On the other hand, in the second speed traveling state in which the second roller 37 is engaged with the input raceway surface 35 and the output raceway surface 40, in the first speed gear pair 7, the driven gear 7b is driven and the drive gear 7a is driven. On the side. In this case, as shown in FIG. 8A, axial forces in opposite directions (in the direction of arrow A and the direction of arrow P in FIG. 8A) are generated in the driving gear 7a and the driven gear 7b, respectively. This axial force acts simultaneously with the driven gear 7b becoming the driving side and the driving gear 7a becoming the driven side, so that the first outer ring 29 is pulled away from the first inner ring 24 and the first outer ring 29 by the rotation of the first roller 27. Acts quickly. As a result, the track interval between the input track surface 25 and the output track surface 30 can be increased quickly, so that the engagement between the input track surface 25 and the output track surface 30 and the first roller 27 can be quickly performed.

  When the first inner ring 24 and the first outer ring 29 are rotated relative to each other (free rotation), in addition to the pulling force of the input raceway surface 25 and the output raceway surface 30 due to the rotation of the first roller 27, the drive gear 7a and the driven gear An axial force in the opposite direction (in the direction of arrow A in FIG. 8A) due to 7 b acts on the first outer ring 29. As a result, the distance between the input raceway surface 25 and the output raceway surface 30 is widened by the axial force acting on the drive gear 7a, more than the first inner ring 24 and the first outer ring 29 are separated by the separating force due to the rotation of the first roller 27. Can do. Thereby, the torque when the 1st inner ring 24 and the 1st outer ring 29 carry out relative rotation (free rotation) can be reduced.

  Next, referring to FIG. 8B, the friction between the tooth surfaces of the drive gear 8a and the driven gear 8b will be examined. When the drive gear 8a is rotated in one direction (the direction of the arrow Ro in FIG. 8B), the circumferential force N in the plane perpendicular to the axis acts on the tooth surface of the drive gear 8a by the reaction force of the driven gear 8b. On the other hand, the circumferential force N in the plane perpendicular to the axis also acts on the tooth surface of the driven gear 8b. The circumferential force N is decomposed into a tangential force F perpendicular to the central axis O and an axial force S parallel to the central axis O. If the torsion angle of the drive gear 8a is β, the axial force S is expressed by equation (1).

S = N · sin β Formula (1)
Further, if the friction coefficient between the tooth surfaces of the drive gear 8a and the driven gear 8b is μ, the axial component force S ′ of the friction force caused by the tooth surfaces of the drive gear 8b is expressed by Expression (2).

S ′ = μN · cos β Formula (2)
Here, in order to move the second outer ring 39 in the axial direction (direction of arrow A in FIG. 8 (b)) so as to narrow the distance between the input raceway surface 35 and the output raceway surface 40, the drive gear 8a with respect to the driven gear 8b. Must be moved in the axial direction (the direction of arrow A in FIG. 8B). For this purpose, it is necessary that the absolute value of the axial force S is larger than the absolute value of the axial component S ′ of the frictional force, that is, the expression (3) must be established. Since S> 0 and S ′> 0, the absolute value symbol is omitted in Equation (3).

S-S '> 0 ... Formula (3)
When the equations (1) and (2) are substituted into the equation (3) and solved, the equation (4) is derived.

μ <tan β Formula (4)
If the friction coefficient μ between the tooth surfaces of the drive gear 8a and the driven gear 8b and the torsion angle β of the drive gear 8a are set as shown in the equation (4), the drive gear 8a is axially moved with respect to the driven gear 8b ( It can be moved in the direction of arrow A in FIG. Accordingly, the second outer ring 39 can be moved in the axial direction (direction of arrow A in FIG. 8 (b)) so as to narrow the distance between the input raceway surface 35 and the output raceway surface 40, so that the drive gear 8a and the driven gear 8b It is possible to prevent the pulling force in the axial direction of the second inner ring 34 and the second outer ring 39 from being suppressed by the friction between the tooth surfaces. Thereby, the clutch apparatus 20 can transmit predetermined torque reliably.

  Further, since the drive gear 8a and the driven gear 8b are constituted by helical gears, the strength can be increased as compared with a spur gear of the same size, and rotational power can be transmitted quietly. In addition, high-speed rotation can be transmitted, and the combination of the number of teeth of the driving gear 8a and the driven gear 8b is not limited and excellent in flexibility.

  Next, a second embodiment will be described with reference to FIGS. In the first embodiment, the case where the clutch device 20 is made incapable of engagement by reducing the protruding amount of the pins 61 and 62 by the camshaft 50 has been described. On the other hand, in the second embodiment, a case will be described in which the clutch device 120 is made unengageable by increasing the amount of protrusion of the pins 161 and 162 from the input shaft 4 by the camshaft 150. In addition, about the part same as the part demonstrated in 1st Embodiment, the same code | symbol is attached | subjected and the following description is abbreviate | omitted.

  Here, FIG. 9A is a sectional side view of the clutch device 120 constituting the transmission according to the second embodiment, and FIG. 9B is a diagram of the clutch device 120 in which the camshaft 150 is moved in the axial direction. FIG. 9C is a half sectional view of the clutch device 120 in which the first roller 27 is engaged. 10A is a half sectional view of the clutch device 120 in which the camshaft 150 is moved in the axial direction, and FIG. 10B is a half sectional view of the clutch device 120 in which the second roller 37 is engaged. FIG. 10C is a half sectional view of the clutch device 120 in a state where the engagement of the first roller 27 is released.

  As shown in FIG. 9A, when the transmission of the power of the input shaft 4 is interrupted, the clutch device 120 causes the pins 161 and 162 to protrude from the input shaft 4 by the cam portions 151 and 162 of the camshaft 150, thereby The pins 161 and 162 are pressed against the inclined surfaces 124 b and 134 b formed on the inner ring 124 and the second inner ring 134. As a result, the first inner ring 124 and the second inner ring 134 move inward in the axial direction, and the first inner ring 124 and the second inner ring 134 come into contact with the stopper 22. As a result, the track interval is secured and the first roller 27 and the second roller 37 cannot be engaged, so that the power transmission of the input shaft 4 is interrupted.

  As shown in FIG. 9B, when traveling at the first speed, the camshaft 150 is moved to one side in the axial direction (left side in FIG. 9) to reduce the protruding amount of the pin 161 from the input shaft 4. The protrusion of the pin 162 from the input shaft 4 is maintained. As a result, the restriction of the first inner ring 124 is released, and the first inner ring 124 is moved to the stopper 21 side by the disc spring 126. As a result, the track interval between the first inner ring 124 and the first outer ring 29 is reduced, and the first roller 27 is in an engageable state.

  By rotating the first roller 27, as shown in FIG. 9C, the track interval between the first inner ring 124 and the first outer ring 29 is further reduced, and the first roller 27 is moved to the first inner ring 124 and the first outer ring. 29 is engaged. As a result, the rotational power of the input shaft 4 is transmitted to the first outer ring 29 and the drive gear 7a, and the output shaft 5 rotates by the meshing of the gear pair 7 (see FIG. 1).

  When traveling at the second speed as shown in FIG. 10A, the pin 161 protrudes from the input shaft 4 by moving the camshaft 150 to one side in the axial direction (left side in FIG. 10). The amount of protrusion from the input shaft 4 is reduced. As a result, the restriction on the second inner ring 134 is released, and the second inner ring 134 is moved to the stopper 23 side by the disc spring 136. As a result, the track interval between the second inner ring 134 and the second outer ring 39 is narrowed, and the second roller 37 can be engaged.

  By rotating the second roller 37, as shown in FIG. 10 (b), the track interval between the second inner ring 134 and the second outer ring 39 is further reduced, and the second roller 37 is moved to the second inner ring 134 and the second outer ring. 39 is engaged. As a result, the rotational power of the input shaft 4 is transmitted to the second outer ring 39 and the drive gear 8a, and the output shaft 5 rotates by meshing of the gear pair 8 (see FIG. 1).

  When the second outer ring 39 moves toward the stopper 22 by the engagement of the second roller 37, the coil spring 33 is compressed. Due to the reaction force of the coil spring 33 and the relative rotation of the first outer ring 29 with respect to the first inner ring 124, the second outer ring 39 is moved to one axial side (left side in FIG. 10) as shown in FIG. . Thereby, a track | orbit space | interval is ensured and the 1st roller 27 and the 2nd roller 37 cannot be engaged. According to the second embodiment described above, the same operational effects as those of the first embodiment can be realized.

  In addition, the first inner ring 124 and the second outer ring 29 (the second inner ring 134 and the second outer ring 39) and the first inner ring 124 and the second outer ring 29 in a direction in which the first roller 27 (the second roller 37) can be engaged with each other. The inner ring 134 is biased by the disc springs 126 and 136 (elastic members). Thereby, the clutch device 120 can be easily engaged. On the other hand, the first roller 27 and the second roller 37 are moved by moving the first inner ring 124 and the second inner ring 134 in the axial direction against the biasing force of the disc springs 126 and 136 by the axial movement of the camshaft 150. Can be disengaged. As a result, the engagement of the clutch device 120 can be reliably released. Note that the elastic members for urging the first inner ring 124 and the second inner ring 134 in the axial direction are not limited to the disc springs 126 and 136, and other elastic members such as a coil spring can be used as a matter of course.

  Next, a third embodiment will be described with reference to FIG. In the first and second embodiments, the case where the clutch devices 20 and 120 are engaged and disengaged by the axial movement of the camshafts 50 and 150 provided in the input shaft 4 has been described. On the other hand, in the third embodiment, a case will be described in which the clutch device 220 is engaged and disengaged by the axial movement of the shift fork 250 arranged radially outside the input shaft 4. In addition, about the part same as the part demonstrated in 1st Embodiment, the same code | symbol is attached | subjected and the following description is abbreviate | omitted. FIG. 11A is a half sectional view of the clutch device 220 constituting the transmission according to the third embodiment, and FIG. 11B is a half sectional view of the clutch device 220 in which the first roller 27 is engaged. FIG. 11C is a half sectional view of the clutch device 220 in which the second roller 37 is engaged.

  As shown in FIG. 11A, in the clutch device 220, a shift fork 250 is disposed at a position where the first inner ring 224 and the second inner ring 234 are adjacent to each other. The shift fork 250 is a member for moving the first inner ring 224 and the second inner ring 234 in the axial direction along the input shaft 4, and a base portion is fixed to the shaft portion 251. The shaft portion 251 is a shaft-like member disposed in parallel with the input shaft 4, and the shift fork 250 moves along the input shaft 4 by being moved in the axial direction by a driving device (not shown). An elastic member (not shown) that biases the shift fork 250 in the moving direction of the shaft portion 251 is interposed between the drive device (not shown) and the shaft portion 251.

  When the transmission of power from the input shaft 4 is cut off, the shift fork 250 is in the neutral position. As a result, the first inner ring 224 and the second inner ring 234 are biased by the disc springs 226 and 236 and the inner end surfaces in the axial direction abut against each other. As a result, the track interval is secured and the first roller 27 and the second roller 37 cannot be engaged, so that the power transmission of the input shaft 4 is interrupted.

  As shown in FIG. 11B, when traveling at the first speed, the shift fork 250 is moved to one side in the axial direction (left side in FIG. 11). As a result, the first inner ring 224 moves to the stopper 21 side (drive gear 7a side) against the urging force of the disc spring 226. As a result, the track interval between the first inner ring 224 and the first outer ring 29 is reduced, and the first roller 27 is in an engageable state.

  As the first roller 27 rotates, the track interval between the first inner ring 224 and the first outer ring 29 is further reduced. Further, since the first inner ring 224 is urged in the moving direction (left side in FIG. 11) of the shaft portion 251 by an elastic member (not shown), the track interval gradually decreases, and finally the first roller 27 is moved to the first inner ring. 224 and the first outer ring 29 are engaged. As a result, the rotational power of the input shaft 4 is transmitted to the first outer ring 29 and the drive gear 7a, and the output shaft 5 rotates by the meshing of the gear pair 7 (see FIG. 1).

  As shown in FIG. 11C, when traveling at the second speed, the shift fork 250 is moved to the other side in the axial direction (right side in FIG. 11). As a result, the second inner ring 234 moves to the stopper 23 side (drive gear 8a side) against the urging force of the disc spring 236. As a result, the track interval between the second inner ring 234 and the second outer ring 39 is narrowed, and the second roller 37 can be engaged.

  By rotating the second roller 37, the track interval between the second inner ring 224 and the second outer ring 39 is further reduced. Further, since the second inner ring 234 is urged in the moving direction (right side in FIG. 11) of the shaft portion 251 by an elastic member (not shown), the track interval gradually decreases, and the second roller 37 finally becomes the second inner ring. 234 and the second outer ring 39 are engaged. As a result, the rotational power of the input shaft 4 is transmitted to the second outer ring 39 and the drive gear 8a, and the output shaft 5 rotates by meshing of the gear pair 8 (see FIG. 1).

  On the other hand, when the shift fork 250 moves to the other side in the axial direction (the right side in FIG. 11), the first inner ring 224 is driven by the biasing force of the disc spring 226 and the relative rotation of the first outer ring 29 with respect to the first inner ring 224. Move to the other side of the direction (right side of FIG. 11). As a result, the track interval is secured, and the first roller 27 cannot be engaged with the first inner ring 224 and the first outer ring 29. According to the third embodiment described above, the clutch fork 220 is switched between engagement and disengagement by the shift fork 250 disposed on the radially outer side of the input shaft 4, so that the structure of the transmission is simplified. it can.

  Next, a fourth embodiment will be described with reference to FIG. In the first to third embodiments, the case where the drive gears 7a to 14a are supported by the clutch devices 20, 120, and 220 has been described. In contrast, in the fourth embodiment, a case where the driven gears 7b to 14b are supported by the clutch device 20 will be described. In addition, about the part same as 1st Embodiment, the same code | symbol is attached | subjected and the following description is abbreviate | omitted.

  FIG. 12A is a skeleton diagram schematically showing the transmission 301 in the fourth embodiment, and FIG. 12B is a schematic diagram showing the rotational direction and the thrust direction in the meshing of the gear pair 8. In FIG. 12A, illustration of the other gear pairs 9 to 14 constituting the transmission is omitted, and in FIG. 12B, illustration of the second inner ring 34 and the second roller 37 is omitted. Part of the teeth 8a2 and 8b2 formed on the driving gear 8a and the driven gear 8b are not shown.

  As shown in FIG. 12A, the transmission 301 has a plurality of gear pairs 7 and 8 disposed on a pair of input shaft 304 and output shaft 305, and the driven gears 7b and 8b are connected to the clutch device 20. Are connected to a first outer ring 29 (see FIG. 2) and a second outer ring 39 as input system rotating members. The output shaft 305 is configured such that the camshaft 50 is provided therein, and the engagement or disengagement of the clutch device 20 is switched when the camshaft 50 moves in the axial direction.

  As shown in FIG. 12B, when the input shaft 304 and the drive gear 8a are rotated in the direction of the arrow Rt, the driven gear 8b is driven in the direction of the arrow Ri, and the second outer ring 39 is rotated in the direction of the arrow Ri. When the second roller 37 is engaged with the second outer ring 39 and the second inner ring 34 as an output system rotating member, the rotational power indicated by the arrow Ro is output from the output shaft 305.

  When the driven gear 8b is driven in the direction of the arrow Ri, the circumferential force N in the plane perpendicular to the axis acts on the tooth surface of the driven gear 8b (tooth 8b2) by the reaction force of the driving gear 8a (tooth 8a2). As a result, an axial force S (in the direction of arrow P) is generated in the driven gear 8b and the second outer ring 39. Similarly to the transmission 1, the direction of the axial force S acting on the driven gear 8b (arrow P direction) in the transmission 301 is the same as the moving direction of the second outer ring 39 in the axial direction when the track interval is narrowed. Thus, the twist direction of the tooth trace of the driven gear 8b and the drive gear 8a is set. Thus, the second inner ring 34 and the second outer ring 39 are relatively moved in the axial direction against the axial component of the frictional force generated in the second inner ring 34 and the second outer ring 39 and the second roller 37 of the clutch device 20. Can be attracted. As a result, the predetermined torque can be reliably transmitted by the engagement of the second roller 37.

  When the driven gears 7b and 8b are connected to the first outer ring 29 and the second outer ring 39 as in the fourth embodiment, the output raceway surfaces 30 and 40 of the first outer ring 29 and the second outer ring 39 are The input raceway surfaces function as input raceway surfaces, and the input raceway surfaces 25 and 35 of the first inner ring 24 and the second inner ring 34 function as output raceway surfaces.

  The present invention has been described above based on the embodiments. However, the present invention is not limited to the above embodiments, and various improvements and modifications can be made without departing from the spirit of the present invention. It can be easily guessed. For example, the numerical values (for example, the number and size of each component such as the number of gears) given in the above embodiment are merely examples, and other numerical values can naturally be adopted.

  In the above-described embodiment, the transmissions 1 and 301 having the input shafts 4 and 304 as the first shaft and the output shafts 5 and 305 as the second shaft have been described, but the present invention is not necessarily limited thereto. For example, the present invention can naturally be applied to a transmission (so-called output reduction) in which an input shaft and an output shaft are arranged coaxially and a counter shaft is arranged in parallel with the input shaft and the output shaft. In this transmission (output reduction), the input shaft can be the first shaft and the counter shaft can be the second shaft, and torque can be transmitted from the input shaft to the output shaft via the counter shaft by a gear pair.

  Although not described in the above embodiment, another gear pair is provided on the input shaft 4, 304 and the output shaft 5 305, and the power input from the output shaft 5 305 is transmitted to one gear of the gear pair. While being transmitted to the input shaft 4, 304, it can be configured to be supported by a clutch device that blocks transmission of power from the input shaft 4, 304 to the output shaft 5 305. As a result, during inertial movement in which power is transmitted from the output shaft 5,305 to the input shaft 4,304, power is transmitted from the output shaft 5,305 to the input shaft 4,304 by the clutch device and input from the output shaft 5,305. The shaft 4 and 304 are driven. Since the power source such as the engine becomes the driving resistance of the output shaft 5,305, the output shaft 5,305 can be braked. Therefore, the braking of the output shaft 5,305 is prevented rather than preventing the output amount during inertial movement from decreasing. Can be prioritized.

  The clutch device in this case can employ a clutch device that switches between transmission and interruption of power by engagement of the rollers described in each embodiment. Of course, it is possible to employ a two-way clutch such as a sprag type one-way clutch or a roller type.

  In the above embodiment, the case where the driving gears 7a and 8a and the driven gears 7b and 8b are provided on the outer circumferences of the first outer ring 29 and the second outer ring 39 has been described. However, the present invention is not limited to this. And an axial end surface of the second inner ring 34 is extended in the axial direction, and an extending portion (not shown) extending axially outward from the axial end surfaces of the first outer ring 29 and the second outer ring 39 is provided. It is possible to provide the drive gears 7a and 8a and the driven gears 7b and 8b in the installed portion. A gear pair is formed by the drive gears 7a and 8a and the driven gears 7b and 8b, and the first outer ring 29 and the second outer ring 39 are moved in the axial direction to switch the engagement or disengagement of the cam. As a result, the axial length is increased, but the same effect as the present embodiment can be realized.

  In the above-described embodiment, the case where the input raceway surfaces 25 and 35 and the output raceway surfaces 30 and 40 are formed as single-leaf rotating hyperboloids and the cylindrical first roller 27 and the second roller 37 are employed has been described. Of course, the input raceway surfaces 25 and 35, the output raceway surfaces 30 and 40, the first roller 27, and the second roller 37 in other forms may be employed. As another form, for example, the input raceway surfaces 25 and 35 and the output raceway surfaces 30 and 40 are formed of a single leaf rotating hyperboloid and the first roller 27 and the second roller 37 are conical, and the input raceway surfaces 25 and 35. Further, the output raceway surfaces 30 and 40 have a conical surface, the input raceway surfaces 25 and 35 or the output raceway surfaces 30 and 40 have a cylindrical shape, the first roller 27 and the second roller 37 have a drum shape, a drum shape, The thing etc. which make it cylindrical shape are mentioned.

  Note that the input raceway surfaces 25 and 35 and the output raceway surfaces 30 and 40 are preferably formed as a single-leaf rotating hyperboloid or a conical surface in line contact with the outer peripheral surfaces of the first roller 27 and the second roller 37. This is because the input raceway surfaces 25 and 35 and the output raceway surfaces 30 and 40 can be easily processed by making the raceway surface into a simple conical surface. Moreover, durability can be improved compared with the case where a raceway surface is made into a conical surface by making a raceway surface into a monoplane rotation hyperboloid. That is, when a roller having a skew angle (the first roller 27 or the second roller 37) is engaged with the raceway surface (single leaf hyperboloid), the roller and the raceway surface are separated even if the amount of axial deflection of the roller is small. This is because line contact can be achieved, so that the roller diameter can be increased and the contact area can be increased (the line contact length can be increased).

  In the above embodiment, the case where the gear pairs 6 to 14 are configured by a pair of helical gears (oblique gears) has been described. However, the present invention is not necessarily limited to this, and the gear pairs 6 to 14 are configured by spur gears. Is of course possible.

  In the first embodiment, when the camshaft 50 is provided with the cam portions 51 to 55 corresponding to the gear pairs 7 to 14 (first speed to eighth speed), that is, the cam portion 51 is attached to the gear pairs 7 and 8. The case of corresponding but not corresponding to the other gear pairs 9 to 14 has been described. However, the present invention is not necessarily limited to this, and the cam portion is provided so that the axial position of the specific cam portion corresponds to a plurality of gear pairs, for example, the cam portion 51 only corresponds to the gear pairs 7 and 8. Of course, it is possible to correspond to any of the other gear pairs 9 to 14. This is because the positions of the cam portion and the pins in the circumferential direction and the axial direction may be set as appropriate.

In the third embodiment, an elastic member (not shown) is disposed on the shaft portion 251 and the shift fork 250 is biased in the moving direction of the shaft portion 251 by compressive deformation of the elastic member. However, it is not necessarily limited to this. For example, it is naturally possible to form the arm of the shift fork 250 from an elastic member and bias the shift fork 250 in the moving direction of the shaft portion 251 by bending deformation of the elastic member. Also in this case, the first inner ring 224 and the second inner ring 234 can be urged in the axial direction, and the same effect as the third embodiment can be realized.
<Others>
<Means>
The transmission of the technical idea 1 is arranged on a pair of parallel first shaft and second shaft, and is configured to have a plurality of gear pairs set so as to mesh with each other and to have different gear ratios, and a plurality of gear pairs. While each gear is supported so as to be rotatable relative to the first shaft or the second shaft, the power input from the first shaft is transmitted to the second shaft so as to be cut off, while the second shaft A clutch device that cuts off transmission of power from the first shaft to the first shaft, the clutch device including a gear disposed on the second shaft or an input system rotating member coupled to the first shaft, and an input thereof An output system rotating member connected to the gear disposed on the first shaft or the second shaft and configured to be relatively movable in the axial direction with respect to the system rotating member, and an inner periphery of the output system rotating member The output gauge formed on one of the surface and the outer peripheral surface An input raceway surface that is opposed to the output raceway surface and formed on one of the inner circumferential surface or the outer circumferential surface of the input system rotating member, and is interposed between the input raceway surface and the output raceway surface. And a predetermined skew angle with respect to the central axis of the input system rotation member, and a plurality of gears that engage with the input raceway surface and the output raceway surface to transmit power from the first shaft to the second shaft. And a switching means for switching engagement or disengagement of the roller with the input raceway surface and the output raceway surface.
The transmission of the technical idea 2 is the transmission according to the technical idea 1, wherein the input raceway surface and the output raceway surface are formed as a single-leaf rotating hyperboloid or a conical surface in line contact with the outer peripheral surface of the roller. ing.
The transmission of the technical idea 3 is a transmission according to the technical idea 1 or 2, wherein the clutch device is arranged on the input raceway surface and the output raceway surface in a gear pair set to a predetermined speed ratio. Power is transmitted by engaging the rollers, and when shifting up, in the gear pair having a gear ratio smaller than the gear ratio of the gear pair to which power is being transmitted, the switching means causes the input track surface and the output track. The state where the engagement between the surface and the roller is released is switched to the state where the input raceway surface and the output raceway surface are engaged with the roller.
The transmission of technical idea 4 is the transmission according to any one of technical ideas 1 to 3, wherein the gear pair has a twist direction set so that a tooth line is not parallel to the central axis. The twist direction is such that the direction of the axial force acting on the gear by the meshing of the gear pair is such that the distance between the input raceway surface and the output raceway surface is reduced, and the roller is applied to the input raceway surface and the output raceway surface. Is set to be the same as the direction of movement of the input system rotating member or the output system rotating member in the axial direction when they are engaged.
The transmission of the technical idea 5 is the transmission according to any one of the technical ideas 1 to 4, wherein the clutch device is disengaged from the input raceway surface, the output raceway surface, and the roller. An inlay portion that engages with the input system rotating member or the output system rotating member to which the gear is connected in the state is provided, and the inlay portion engages the input raceway surface, the output raceway surface, and the roller. A radial gap that allows rolling of the roller that sometimes occurs is provided between the input system rotating member or the output system rotating member.
The transmission of the technical idea 6 is the transmission according to any one of the technical ideas 1 to 5, wherein the clutch device is disengaged from the input raceway surface, the output raceway surface, and the roller. In the state, the movement restricting portion for restricting the movement of the input rotating member or the output rotating member connected to the gear to one side in the axial direction, and the urging force in the axial direction toward the movement restricting portion And an urging means for applying to the input system rotating member or the output system rotating member.
The transmission of the technical idea 7 is the transmission according to any one of the technical ideas 1 to 6, wherein the input system rotation is performed in a direction in which the input raceway surface, the output raceway surface, and the roller can be engaged with each other. An elastic member that biases at least one of the member and the output system rotating member, and the switching unit moves the input system rotating member or the output system rotating member in the axial direction against the biasing force of the elastic member. And the engagement between the input raceway surface and the output raceway surface and the roller is released.
The transmission of the technical idea 8 is the transmission according to any one of the technical ideas 1 to 7, wherein the switching means can engage or engage the input raceway surface and the output raceway surface with the roller. A moving mechanism is provided for moving the input system rotating member or the output system rotating member to a position in the axial direction where it becomes impossible.
<Effect>
According to the transmission described in the technical concept 1, a plurality of meshing gear pairs arranged on a pair of parallel shafts, one of which is a first shaft and the other is a second shaft, are set to have different gear ratios. Is done. One gear of each of the plurality of gear pairs is supported so as to be rotatable relative to the shaft by a clutch device.
The clutch device is configured such that power input from the first shaft is transmitted to the second shaft so as to be cut off, while transmission of power from the second shaft to the first shaft is cut off. The output system rotating member is configured to be relatively movable in the axial direction with respect to the input system rotating member, and an output track surface is formed on one of the inner peripheral surface and the outer peripheral surface of the output system rotating member. The input raceway surface is formed on one of the inner circumferential surface and the outer circumferential surface of the input system rotating member while facing the output raceway surface. A plurality of rollers are interposed between the input raceway surface and the output raceway surface, and the rollers are set at a predetermined skew angle with respect to the central axis of the input system rotation member. When the roller rotates in a predetermined direction, the roller revolves around the central axis while being rotated by being guided by the input raceway surface and the output raceway surface.
Guided by the rotation of the roller, the input system rotating member and the output system rotating member move relative to each other in the direction in which the distance between the input track surface and the output track surface is reduced while being elastically deformed in the radial direction. As a result, the rollers engage with the input raceway surface and the output raceway surface, and power is transmitted from the first shaft to the second shaft. When the clutch device on the high speed stage side, which has been disengaged from the input raceway surface and the output raceway surface, and the roller is engaged by the switching means, the low speed stage clutch device to which torque has been transmitted so far becomes the one-way clutch. The roller engagement is automatically released. Therefore, it is possible to eliminate the time during which torque transmission is interrupted when changing the gear ratio.
Here, when switching from the disengaged state to the engaged state by the switching means, the input system rotating member and the output system rotating member are elastically deformed in the radial direction, and the distance between the input track surface and the output track surface is reduced. The rollers move relative to each other in the axial direction, and the rollers engage with the input raceway surface and the output raceway surface. Since the input rotation member and the output rotation member are elastically deformed in the radial direction, the change in the input rotation speed accompanying the change in the gear ratio can be mitigated. Shock can be suppressed. Therefore, there is an effect that the shock of shifting can be suppressed while eliminating the time during which the torque transmission is interrupted.
According to the transmission described in the technical idea 2, the input raceway surface and the output raceway surface are formed as a single-leaf rotating hyperboloid or a conical surface in line contact with the outer peripheral surface of the roller. By making the shape of the input raceway surface and the output raceway surface into simple conical surfaces, in addition to the effect of the technical idea 1, there is an effect that machining can be facilitated. In addition, by making the input raceway surface and the output raceway surface a single leaf rotation hyperboloid, it is easier to make a contact between the roller having the skew angle and the raceway surface than in the case where the raceway surface is a conical surface. As a result, the durability can be improved.
According to the transmission described in the technical idea 3, in a gear pair set to a predetermined gear ratio, power is transmitted by engaging a roller with an input raceway surface and an output raceway surface by a clutch device. When shifting up, in the gear pair having a gear ratio smaller than the gear ratio of the gear pair to which power is transmitted, the input track is changed from the state where the engagement between the input track surface and the output track surface and the roller is released by the switching means. The surface and the output raceway surface are switched to a state where the rollers are engaged. When the power is transmitted from the gear pair having a small gear ratio after being shifted up, the rotation speed of the second shaft increases as compared to before the shift up. As a result, in the clutch device in the gear pair to which power was transmitted before the upshift, the output system rotating member rotates relative to the input system rotating member, so that it acts as a one-way clutch and automatically Is interrupted. As a result, the shifting can be performed by switching from the state where the engagement between the input raceway surface and the output raceway surface and the roller is released to the state where the input raceway surface and the output raceway surface are engaged with the roller. As a result, in addition to the effects of the technical idea 1 or 2, there is an effect that it is possible to eliminate the time during which torque transmission is interrupted at the time of upshifting.
According to the transmission described in the technical idea 4, the torsional direction of the gear pair is set so that the teeth are not parallel to the central axis, and the torsional direction acts on the gear by the meshing of the gear pair. The direction of the axial force when the input system rotating member or the output system rotating member moves in the axial direction when the distance between the input track surface and the output track surface is reduced and the rollers are engaged with the input track surface and the output track surface. Are set to be the same.
Here, when the rollers engage with the input raceway surface and the output raceway surface, the shafts of the input system rotation member and the output system rotation member are generated by the axial component of the frictional force generated between the input raceway surface, the output raceway surface, and the rollers. The pulling force in the direction is suppressed. If the axial component force increases, the distance between the input raceway surface and the output raceway surface cannot be sufficiently narrowed, and a predetermined torque may not be transmitted.
On the other hand, the twist direction of the gear teeth of the gear pair reduces the distance between the input raceway surface and the output raceway surface, and the input system rotating member or output in the axial direction when the rollers engage with the input raceway surface and the output raceway surface. By setting the direction of movement of the system rotation member to be the same, when the rollers are engaged with the input raceway surface and the output raceway surface and power is transmitted, the input system rotation member or output system is generated by the reaction force of the gear. The rotation member is promoted to move in the axial direction so as to narrow the distance between the input raceway surface and the output raceway surface. Thereby, the pulling force in the axial direction of the input system rotating member and the output system rotating member can be increased, and in addition to any one of the technical ideas 1 to 3, there is an effect that a predetermined torque can be reliably transmitted.
According to the transmission described in the technical idea 5, the clutch device includes an input system rotating member or an output system rotating member to which a gear is coupled in a state where the input raceway surface and the output raceway surface are disengaged from the rollers. An inlay portion to be fitted is provided. The inlay portion has a radial clearance between the input system rotating member or the output system rotating member that allows the rollers to roll when the input track surface and the output track surface engage with the rollers. Therefore, it is possible to suppress the engagement of the input raceway surface and the output raceway surface with the rollers by the inlay portion. In addition, in the state where the engagement between the input raceway surface and the output raceway surface and the roller is released, the radial movement of the input system rotation member or the output system rotation member is restricted. In addition to this effect, there is an effect that noise generated when the gear rotates relative to the clutch device can be prevented.
According to the transmission described in the technical idea 6, in the state where the input raceway surface and the output raceway surface are disengaged from the rollers, the axial direction of the input system rotary member or the output system rotary member to which the gears are coupled is released. Movement to one side is restricted by the movement restricting portion, and an urging force in the axial direction toward the movement restricting portion is applied to the input system rotating member or the output system rotating member by the urging means. Thus, in the state where the engagement between the input raceway surface and the output raceway surface and the roller is released, the axial movement of the input system rotation member or the output system rotation member is restricted, and the clutch device is kept in the non-engagement state. be able to.
Thereby, in addition to the effect of any one of the technical ideas 1 to 5, it has a fail-safe function even when the shift system member or the control system breaks down, and can prevent double meshing in which a plurality of gear pairs are engaged simultaneously. effective. In addition, the clutch device other than the gear pair to which torque is transmitted is kept in the non-engaged state without inputting an electric signal, so that it is possible to reduce power consumption and reduce friction.
According to the transmission described in the technical concept 7, at least one of the input system rotating member and the output system rotating member is urged by the elastic member in a direction in which the input raceway surface, the output raceway surface, and the roller can be engaged. The Thus, in addition to any one of the technical ideas 1 to 6, there is an effect that the clutch device can be easily engaged. On the other hand, when the input system rotating member or the output system rotating member is moved in the axial direction by the switching means against the biasing force of the elastic member, the engagement between the input track surface and the output track surface and the roller is released. Therefore, there is an effect that the engagement between the input raceway surface and the output raceway surface and the roller can be reliably released.
According to the transmission described in the technical idea 8, the input system rotation member or the output system rotation member moves to an axial position where the input raceway surface, the output raceway surface, and the roller can be engaged or cannot be engaged by the moving mechanism. Therefore, transmission of power from the input system rotating member to the output system rotating member can be blocked. As a result, in addition to any one of the technical ideas 1 to 7, there is an effect that power can be transmitted from the input system rotating member to the output system rotating member so as to be cut off.

1,301 Transmission 4,304 Input shaft (first shaft)
5,305 Output shaft (second axis)
7,8,9,10,11,12,13,14 Gear pair 20, 120, 220 Clutch device 21a, 23a Inlay part 21b, 23b Ridge part (movement restriction part)
24 1st inner ring (input system rotating member or output system rotating member)
25, 35 Input raceway surface 27 First roller (roller)
29 1st outer ring (output system rotating member or input system rotating member)
30, 40 Output raceway surface 33 Coil spring (biasing means)
34 Second inner ring (input system rotating member or output system rotating member)
37 Second Roller (roller)
39 Second outer ring (output system rotating member or input system rotating member)
50,150 Camshaft (part of switching means and moving mechanism)
60 Drive device (switching means and part of moving mechanism)
124, 224 First inner ring (input system rotating member)
126,136 Belleville spring (elastic member)
134,234 Second inner ring (input system rotating member)
250 shift fork (switching means and part of moving mechanism)
O Center axis

Claims (8)

A plurality of gear pairs arranged on a pair of parallel first shaft and second shaft and set to have different gear ratios meshing with each other;
To support the plurality of gear pairs gear arranged on the first axis of the can relatively rotate against the first shaft, it can block the power input from the first shaft to the second shaft A clutch device for cutting off transmission of power from the second shaft to the first shaft,
The clutch device,
An input system rotating member connected before Symbol first axis,
With the relative movable in the axial direction with respect to the input system rotating member, and an output system rotating member connected to the tooth wheel arranged on the first shaft,
An output raceway surface formed on the inner peripheral surface of the output system rotating member;
An input raceway surface formed on the outer circumferential surface of the input system rotating member with facing the output track surface,
It is interposed between the input raceway surface and the output raceway surface and set to a predetermined skew angle with respect to the central axis of the input system rotating member, and engages with the input raceway surface and the output raceway surface. A plurality of rollers for transmitting power from the first shaft to the second shaft;
Switching means for switching engagement or disengagement between the roller and the input raceway surface and the output raceway surface;
The gear pair is set in a twist direction so that the tooth traces are not parallel to the central axis, and the twist direction is determined by the direction of the axial force acting on the gear by the engagement of the gear pair. set to be the same as the moving direction of the front SL output system rotating member that put the axial direction when the roller on the input raceway surface and the output track surface by narrowing the intervals of the input raceway surface and the output track surface is engaged Transmission characterized by being made. A plurality of gear pairs arranged on a pair of parallel first shaft and second shaft and set to have different gear ratios meshing with each other;
With a plurality of gears disposed on the second axis of the gear pair for rotatably supported relative to said second axis, capable block the power input from the first shaft to the second shaft A clutch device for cutting off transmission of power from the second shaft to the first shaft,
The clutch device
An input system rotating member connected to the tooth wheel arranged on the second shaft,
With their relative movable in the axial direction with respect to the input system rotating member, and an output system rotating member connected before Symbol second axis,
An output raceway surface formed on the outer peripheral surface of the output system rotating member,
An input raceway surface facing the output raceway surface and formed on the inner peripheral surface of the input system rotating member;
It is interposed between the input raceway surface and the output raceway surface and set to a predetermined skew angle with respect to the central axis of the input system rotating member, and engages with the input raceway surface and the output raceway surface. A plurality of rollers for transmitting power from the first shaft to the second shaft;
Switching means for switching engagement or disengagement between the roller and the input raceway surface and the output raceway surface;
The gear pair is set in a twist direction so that the tooth traces are not parallel to the central axis, and the twist direction is determined by the direction of the axial force acting on the gear by the engagement of the gear pair. the roller is set to be the same as the moving direction of the input system rotating member in the axial direction when engaging the interval of the input raceway surface and the output track surface to said input raceway surface and the output track surface narrows A transmission characterized by comprising: A plurality of gear pairs arranged on a pair of parallel first shaft and second shaft and set to have different gear ratios meshing with each other;
To support the plurality of gear pairs gear arranged on the first axis of the can relatively rotate against the first shaft, it can block the power input from the first shaft to the second shaft A clutch device for cutting off transmission of power from the second shaft to the first shaft,
The clutch device,
An input system rotating member connected before Symbol first axis,
With the relative movable in the axial direction with respect to the input system rotating member, and an output system rotating member connected to the tooth wheel arranged on the first shaft,
An output raceway surface formed on the inner peripheral surface of the output system rotating member;
An outer peripheral surface while the formed input raceways of the input system rotating member with facing the output track surface,
It is interposed between the input raceway surface and the output raceway surface and set to a predetermined skew angle with respect to the central axis of the input system rotating member, and engages with the input raceway surface and the output raceway surface. A plurality of rollers for transmitting power from the first shaft to the second shaft;
Switching means for switching engagement or disengagement between the roller and the input raceway surface and the output raceway surface;
The clutch device includes a spigot portion fitted before SL output system rotating member to which the gear in a state where engagement between the roller and the input raceway surface and the output track surface is released is linked,
Its spigot portion, a radial clearance to permit rolling of the roller caused when the input raceway surface and the output track surface and said roller engages, has between the front SL output system rotating member A transmission characterized by the above. A plurality of gear pairs arranged on a pair of parallel first shaft and second shaft and set to have different gear ratios meshing with each other;
With a plurality of gears disposed on the second axis of the gear pair for rotatably supported relative to said second axis, capable block the power input from the first shaft to the second shaft A clutch device for cutting off transmission of power from the second shaft to the first shaft,
The clutch device
An input system rotating member connected to the tooth wheel arranged on the second shaft,
With their relative movable in the axial direction with respect to the input system rotating member, and an output system rotating member connected before Symbol second axis,
An output raceway surface formed on the outer peripheral surface of the output system rotating member,
An input raceway surface facing the output raceway surface and formed on the inner peripheral surface of the input system rotating member;
It is interposed between the input raceway surface and the output raceway surface and set to a predetermined skew angle with respect to the central axis of the input system rotating member, and engages with the input raceway surface and the output raceway surface. A plurality of rollers for transmitting power from the first shaft to the second shaft;
Switching means for switching engagement or disengagement between the roller and the input raceway surface and the output raceway surface;
The clutch device comprises a socket portion for mating with the input system rotating member engaging said gear in the released state are connected between the said input raceway surface and the output track surface rollers,
Its spigot portion, a radial clearance to permit rolling of the roller caused when the input raceway surface and the output track surface and said roller engages, has between the input system rotating member A transmission characterized by the above. A plurality of gear pairs arranged on a pair of parallel first shaft and second shaft and set to have different gear ratios meshing with each other;
To support the plurality of gear pairs gear arranged on the first axis of the can relatively rotate against the first shaft, it can block the power input from the first shaft to the second shaft A clutch device for cutting off transmission of power from the second shaft to the first shaft,
The clutch device,
An input system rotating member connected before Symbol first axis,
With the relative movable in the axial direction with respect to the input system rotating member, and an output system rotating member connected to the tooth wheel arranged on the first shaft,
An output raceway surface formed on the inner peripheral surface of the output system rotating member;
An input raceway surface formed on the outer circumferential surface of the input system rotating member with facing the output track surface,
It is interposed between the input raceway surface and the output raceway surface and set to a predetermined skew angle with respect to the central axis of the input system rotating member, and engages with the input raceway surface and the output raceway surface. A plurality of rollers for transmitting power from the first shaft to the second shaft;
Switching means for switching engagement or disengagement between the roller and the input raceway surface and the output raceway surface;
Moving the clutch device, in a state where the engagement between the roller and the input raceway surface and the output track surface is released, for regulating the axial direction of the move before SL output system rotating member to which the gear is connected The regulatory department,
Transmission, characterized in that it comprises a biasing means for applying a biasing force in the axial direction to the movement restricting portion before SL output system rotating member. A plurality of gear pairs arranged on a pair of parallel first shaft and second shaft and set to have different gear ratios meshing with each other;
With a plurality of gears disposed on the second axis of the gear pair for rotatably supported relative to said second axis, capable block the power input from the first shaft to the second shaft A clutch device for cutting off transmission of power from the second shaft to the first shaft,
The clutch device
An input system rotating member connected to the tooth wheel arranged on the second shaft,
With their relative movable in the axial direction with respect to the input system rotating member, and an output system rotating member connected before Symbol second axis,
An output raceway surface formed on the outer peripheral surface of the output system rotating member,
An input raceway surface facing the output raceway surface and formed on the inner peripheral surface of the input system rotating member;
It is interposed between the input raceway surface and the output raceway surface and set to a predetermined skew angle with respect to the central axis of the input system rotating member, and engages with the input raceway surface and the output raceway surface. A plurality of rollers for transmitting power from the first shaft to the second shaft;
Switching means for switching engagement or disengagement between the roller and the input raceway surface and the output raceway surface;
Moving the clutch device, in a state where the engagement between the roller and the input raceway surface and the output track surface is released, for regulating the axial direction of the moving of the input system rotating member, wherein the gear is connected The regulatory department,
Transmission, wherein a biasing force in the axial direction to the movement restricting portion and a biasing means for applying to said input system rotating member. A plurality of gear pairs arranged on a pair of parallel first shaft and second shaft and set to have different gear ratios meshing with each other;
To support the plurality of gear pairs gear arranged on the first axis of the can relatively rotate against the first shaft, it can block the power input from the first shaft to the second shaft A clutch device for cutting off transmission of power from the second shaft to the first shaft,
The clutch device,
An input system rotating member connected before Symbol first axis,
With the relative movable in the axial direction with respect to the input system rotating member, and an output system rotating member connected to the tooth wheel arranged on the first shaft,
An output raceway surface formed on the inner peripheral surface of the output system rotating member;
An input raceway surface formed on the outer circumferential surface of the input system rotating member with facing the output track surface,
It is interposed between the input raceway surface and the output raceway surface and set to a predetermined skew angle with respect to the central axis of the input system rotating member, and engages with the input raceway surface and the output raceway surface. A plurality of rollers for transmitting power from the first shaft to the second shaft;
Switching means for switching engagement or disengagement between the roller and the input raceway surface and the output raceway surface;
And an elastic member and the input raceway surface and the output track surface and the roller is to urge the front SL output system rotating member in a direction to be engageable,
It said switching means, wherein the pre-SL output system rotating member against the urging force of the elastic member is moved in the axial direction to release the engagement between the roller and the input raceway surface and the output track surface A transmission. A plurality of gear pairs arranged on a pair of parallel first shaft and second shaft and set to have different gear ratios meshing with each other;
With a plurality of gears disposed on the second axis of the gear pair for rotatably supported relative to said second axis, capable block the power input from the first shaft to the second shaft A clutch device for cutting off transmission of power from the second shaft to the first shaft,
The clutch device
An input system rotating member connected to the tooth wheel arranged on the second shaft,
With their relative movable in the axial direction with respect to the input system rotating member, and an output system rotating member connected before Symbol second axis,
An output raceway surface formed on the outer peripheral surface of the output system rotating member,
An input raceway surface facing the output raceway surface and formed on the inner peripheral surface of the input system rotating member;
It is interposed between the input raceway surface and the output raceway surface and set to a predetermined skew angle with respect to the central axis of the input system rotating member, and engages with the input raceway surface and the output raceway surface. A plurality of rollers for transmitting power from the first shaft to the second shaft;
Switching means for switching engagement or disengagement between the roller and the input raceway surface and the output raceway surface;
And an elastic member and the input raceway surface and the output track surface and the roller is to urge the engageable become direction to said input system rotating member,
It said switching means, characterized in that the against the biasing force of the elastic member moves the input system rotating member in the axial direction to release the engagement between the roller and the input raceway surface and the output track surface A transmission.

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